Metal-working machine.



B. IVI. W. HANSON, METAL WORKING MACHINE.

APPLCATION FILED OCT. 9. 19H.

Patented June 26, 1917 8 SHEETS-SHEET l.

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4 METAL WORMNG MACHINE.

PPLlCATlON FILED OCT. 9. QlL.

1,2319925@ @armed um 26, 191?.

8 SHEETS-SHEET Z ff )WM/L.

B. IVI III!l HANSUII.

METAL WORKING MAcHmE. APPLICATION FILED OCT. 9. 1914. 1 @Si 92555@ Pntcnteune 26, 1917.v

Y 9; 8 SHEETS-SHEET 4.

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l l I I I I I I I B. [VL W, HANSGN.

METAL WGRIHNG MACE-HNE.

APPLSCATION HLEL" OCT. 9i 19H.

Entented June 26, 1917.

8 SHEETS-SHEET 5.

Humm i MLQMX ik@ www; maf

B. IVI. W. HANSUN.

METAL WORKING MACHINE.

APPLlcATIoN FILED ocT. 9. 1914.

1 ,23 1 ,255 Patented June 26, 1917.

8 SHEETS-SHEET 6.

B. M. VV. HANSON.,

METAL WORKING MAGHINEX/ APJUCATION HLED OCT. 9, $914.

'L s l Q 1,231,255. htnedune 2b, LH?.

8 SHEETS-SHEET 7.

B. M. W. HANSON.

METAL WORKING MACHINE.

PPLICATioN FILED ocT. 9, 1914.

l 23 1,255 u' Patented June 26, 1917.

8 SHEETS-SHEET 8.

llllllll @hllillQe BENG'I M. VJ. HSON, 0F HARTFORD, CONNECTCUT;

METAL-WORKING MACHINE.

Specification at' Letters Patent,

Fatented June 26, 193i?.

Application filed @retener 9, 1.93.4. Serial No. $65,855.

To all whom 'i1/ may concern.'

Be it known that l, ,Renoir M, iV. HArisoN, a citizen of the `nited States, residing at Hartford, in the county of Hartford and State of Connecticut, have invented certain new and useful lmprovements in Metal- AViorking Machines, of whicli the following` is a specification.

rlhis invention relates to metal-working machines. My improvements in whole or in part can be incorporated in various kinds of inetal-working machines. in the drawings accomlmnying and forming part o1"I the nesent specihoationl have shown in derail one of the several convenient forms of embodiment of the invention, which to enable those skilled inthe art to practice the same will be set forth fully in the following description. l do not restrict myself to this showing; l may depart therefrom in several respects within the scope oiE the invention defined by the claims following said description.

ln this particular showing, however, the improvements are shown as incorporated in amil]ing-machine.. One of the primary purposes in view is the provision of eiieetive means whereby ay carrier :tor the work or otherwise can be driven either reciprocally or otherwise at different speeds. Janother ob]ect is the provision of means for automatically changing at desired times thev speed of movement of the carrier or equivalent element. `The machine involves many other features of novelty and utility, which with the foregoing` will be set lforth at length in said description.

Referring to said drawings:

Figure l is a front elevation of a metall working machine involving my invention.

Fig. is a. side elevation as seen from the right in Fig. l, partly in section with the head-stock, foot-stock and `gear-ease re moved.

3 is a rear elevation of ythe machine witlrthe tivo stocks removed and with the gear-case in section.

Fig. 4 is a horizontal sectional top plan view of the rear portion of the machine and said gear-case. 4

Fig. 5 is a top plan view of a portion of the work-carrier, tool and work, depending stud and a part oi' the cam,.thelatterfbeing shown by, dottedl lines. y

Fig. 6 is a View partly in elevation and shown in Fig.

partly' in vertical section of the elements Fig, l is a front elevation partly in section, of a disk and a controlling-lever.

Fig. 8 is a diagrammatic view illustrative olf said disk, two controlling levers, a. cam drum and the traveling work carrier.

Fig. El is a detail view partly in vertical sectiom ol a portion of the driving mechanism.

Fig. lO is a view in top plan also partly in section, of means whereby the work-oarrier can be manually adjusted.

Li ke characters refer to like parts throughout the several figures, which it will be noted are on different scales.

The various parts of the machine may be sustained hy any suitable framework, that shown for such purpose comprising the base or bed. 2. Supported by said base or bed is a suitable earrier'such as 3 (see 'for instance Figs. l and Q) and which as illustrated consists of a slide mounted ior reciprocation upon the top of the base or bed, the latter as represented being provided with guideways -l to receive the depending tongue 5 of the reciprocatory carrier or slide 3 to which in the present ease the work is connected,

the tool (or tools) being supported inde-' pendently of the carrier. This lari-ier may he reciproeated in any desirable manner, and in addition to this can be driven at'different speeds. for example fastand slow, the organization being such in preference, that the carrier can be operated as maybe desired, for example it may he 'initially given a iast movement7 then a slo and then a iast or these relations may he entirely changed, the possibilities of speed-control being` practically unlimited.

l prefer to eiiiect the reciprocation of the work carrier by a cam-drum. This condition can, of course,A be obtained in other Yays` but the best results are obtained by using' the medium mentioned which by preference always turns in the same direction. A cam-drum such. as (i (Fig. 2l answers satisfactorily my requirements, said cam drum as illustrated heilig fastened to the shaft 7' within the hollow or bed 2. As illustrated said shaft 7 is supported for rotation by the front and rear walls of the base 0r hed, and for a purpose that will hereinafter appeal'-r projecting through the front wall of said hase. This shaft l' as will also here- As soon as the machine is thrown into action,

inafter appear is continuously rotative and as I have practically already observed,- always turns in the same direction. W'hen I speak of the shaft as being continuously rotative, I means while the machine in action. This drum 6 has a peripheral race or groove 8 (Fig. 2) formed for instance by the duplicate projections-.9, said groove S receiving the stud 10 depending from the work-carrier'or slide 3. Said' cam-groove may be considered as comprising two similar spiral portions ll'and 12, the terminals of which coincide or register. The spiral portion 11 acts to move the work-carrier or slide 3 forward, while the spiral portion 12 serves to reverse the carrier or to'return it to its primary or .initial position, the forward stroke of the work-earrier or slide being identical in degree with the rear stroke and each being of-considerable amplitude, so as to permit an attendant to freely connect work with the carrier when in its backward or retracted position, and this without possibility of interfering with the cutter or other too'l. lV hen the depending stud 1() (preferably in the form of an anti-friction roller) is at the rear junction of the two spiral portions 11 and 12, the `work-carrier or slide 3 is 1n its primary position and in readiness to have the work connected therewith.

the stud 1 0 is caused to relatively traverse the spiral portion 11 to thereby advance said work-carrier or slide, the advancing movement continuing until the stud 10 enters the forward end of the spiral portion 12 at which point the carrier is reversed, the

` return movement continuing as the stud 10 relatively traverses the Spiral portion 12 until said `stud reaches Zthe rear junction of the'two spiral portions at whichV point as will hereinafter appear movement of the work carrier or slide is stopped automatically.

It will, therefore, be evident that on each fullturnof the camdrum G, the work carrier or slide 3 is given one complete reciprocation, and as I have already intimated, the forward movement may be fast and the rear slow or vice versa, while on the forward movement the carriage may be successively speeded up and down and the same on the return movement. Preferably, however, this variation in speed is not obtained through the primary influence of the cam-drum. This cam-drum naturally, however, is operated at a variable speedo'r at least may be, because'there may be cases where I should 'fprefer that'the reciprocation Vof the work` carrier throughout its entire movement be slow, or on the contrary that it be a rapid one. The means'shown for effecting such speed control of the cam-drum 6 and'therefore of the work-carrier 3 will be hereinafter set forth.

The work carrier or slide 3 moves in the channel 13 in the upper side of the base or bed At on'e side of the channel 13 (the l left in Fig'. l) is mounted the head-stock ll, while at the opposite side of said channel is reciproeatory carrier 3. The milling cutter 18 usually directly connected with ihe arbor or niai'uli'el :20, the spindle 1T havingy a' collet or chuck 21 to receive one end of said arbor, the opposite ,end thereof fitting a socket in the auxiliary spindle 22, carried by the slide 23 on the foot-stock 1 5 as is somewhat common in `milling-machines- The slides 16 and 23 shown are vertically adjustable to vary the elevation of the main and auxiliary spindles 1T and and for this purpose any desirable means may he provided, for example the feed screws and 2G furnished as shown, with handwheels 27 and 28, the slides having fixed nuts to receive the respective screws as also quite common in the metal-workiiig art. vOn the outer side of the head stock 14: is supported the change gear box 29, inelosing the change gearing 30 and the 'final gear of which rigid with the spindle or shaft 17. The primary element of said change gearing 30 is fastened to the' shaft 31 having fastened to it'fthe pulley 32 driven by a belt 33.

Fastened in ome suitable manner to the rear of the beds (Fig. a) is the boxer case 40, screwsl el being shown as a suitable means fdr mounting said box rigidly in place. Extending entirely through this box 4.0 for example at the top 'thereof 4is the rotary shaft -12 having fastened to it a drum 43 connected by the belt 42 to the palle 13" fastened to the shaft 31l (Fig. '9), sait the guide pulleys l2". Located below aiid in parallelism with the shaft 4 2 is the shaft 44, the two shafts as shown being connected by a train of change gears denoted in a general way by 45. This shaft 44 is sustaiiied by a bearing upon and extends into the 'box ably associated with the elongatedl hub of the vel pinion 52, for sliding movement on elt 42 between its ends passing over said hub, itbeing evident that*the clutch The bevel pinion 52 is in mesh with the bevel gear 53 pinned or otherwise suitably fastened to the rear member of the sectional shaft 5i, the sections of said shaft 5st being .coaxial and as shown the rear section thereof having a reduced portion fitting a socket in the front portion to maintain the sections of said shaft 5st coaxial. The two sections of said shaft 5-'L'are adapted to be clutched together, being in fact normally in this relation and the front section is operatively connected with the cam-drum 6. I might observe at this time that the bevel gear 53 constitutes in the organization shown the primary element of quick-driving mechanism, the primary element of slow-driving mechanism being as shown, the worm gear 56 hereinafter more particularly described. The shaft t4 has rigidly fastened to its inner end the pinion 57 in mesh with the spur gear 5S loose on the shaft 59 mounted within and supported by the sides of the box 40. S'plined or'otherwise suitably secured to the hub of the spur gear 58 for sliding movement thereon and rotation therewith is the clutch-member 60 cooperative with the clutch member 61 pinned or otherwise suitably secured to the shaft 59. 'lllhen the clutch members 60 and 6l are out of engagement the shaft 59 will not be rotated, but when they are in working relation the opposite result follows. The shaft 59 is shown provided with a worm (i2 in mesh with the teeth -of the worm gear 56 loose on the shaft 54.-, which worm gear through the described connections, is driven at a lower speedthan `the bevel gear 53.

The bevel gear 53 and worm gear 56 are adapted to be clutched together, and this clutch may vary decidedly as to character,

although`one of ,pawl-and-ratchet type has been found to be quite satisfactory. The,'pawl-and-ratehet mechanism may be mounted in any desirable manner, although in the present case the ratchet (S3 rigid with the worm gear 56, 4being fastened by screws 64 and pins65 to that face of the worm gear 5G adjacent .the bevel gear As shown the bevel gear is provided near its periphery (Fig. 3) with several pawls 66 pivotally mounted in place, there being as shown four of such` pawls, and their teeth being constantly advancedy by springs p as 67 acting against ,the tails of said'pawls.

By employing a number of pawls with a single, ratchet-Wheel I kcan make the teeth ofthe ratchet wheel as much larger than if I employa single pawl as is the multiple of the pawls, provided the pawls be properly positioned, and this ,multiple in the present case is four. employing` fou r pawls I can make the ratchetwheel teeth four times the strength they would. be if l utilized but a single pawl, which is a feature of considerable importance. The number is not an essential matter, although that shown has been found pute satisfactory. -The pawls are not equidistantly spaced but are so set as to engage coperating teeth at different points, the construction, however, being such that there will always be a pawl practically behind and against the base of a` ratchet tooth so as to provide against loss of time during the slow feed of the work-carrier or slide ln Fig. 3 the pawl at the left is shown behind and against the base of a cooperating tooth, the pawl at the top being one fourth the distance along its tooth, The pawl on the right is shown one half the distance along its tooth, while the pawl at the bottom is shown three-fourths of the distance along its tooth. lt will he understood that when the quick or rapid feed mechanism .is in action, this is accomplished tlnough the primary agency of the bevel-wheel 53, the clutch members 50 and 5l at this time being in engagement. It conceivable and more than likely that the clutch members 60 and (il will be in engagement at the same time, thus causing the-rotation of the worm gear 5G. The worm gear, however, operates at a much lower speed than the bevel gear 53, so that relatively the teeth of the pawls G6 traverse the teeth of the ratchet wheel 63 idly or without accomplishing anything. Should the clutch member 51,' however, be disengaged from the clutch member *50, the rotation ofthe bevel-gear 53 by the bevel-'pinion 52 will be stopped, but the worm gear 5G will continue to rotate owing to the engagement of the clutch members (50 and Gl and as it does so', one of the pawls 6G byengagiug the ratchet (i3 will rotate the bevel gear through the agency of the worm gear 5G thereby through the described mechanism rotating the drum (3 through the connections hereinafter described, slowly and necessarily effecting a correslfiondingly slow movement of the work-carrier.

lVhil'e preferably the machine is initially thrown into action by hand as will hereinafter appear, the changes in speed or velocity of the'work-carrier 3 are preferably automatically accomplished,l for example through the shifting of a plurality of controlling members such levers which control the action of clutches or analogous devicessuch, for instance as the clutch' members 5l and (il to which I have already re. ferred.

Referring now for example to Figs. 2 and That is to say by 4, it will be seen that within the box 40 is a bearing 68, constituting a support for the f three-armed rocker 69 pivoted to said support as at 7U. The intermediate arm 71 of said rocker 69 is forked to straddle the clutch member 51, the branches of the fork having studs 72 to enter the circumferential channel of said clutch member 5l thereby as the rocker 69 oscillatedto shiftsaid clutch member into und out of power transferring relation with the clutch member 51. The arm 73 of said rocker has pivoted to` it the extreme rear end of the rod 74: likewise connected at its forward end to the crank 75 fastened to and rising from the shaft 76 supported for oscillation on the bracket 77 on the front of the bed 2.- To said shaft 7 6 -is fastened the lower end of the. lever 78 shown as occupying its retracted position in Fig. 2. When said lever is in this position the clutch member 51 is disengaged from the clutch member 50. The initial forward movement of the lever 78 is effected by hand, but the final movement is rapidly secured by independent means', excellent results having been obtained. in this connection through the agency= of a spring. The arm 80 of the rocker 69 is bored to receive the springplunger 81 constantly urged forward by the spring 82, the forward or outer end of said spring plunger being beveled to coperate with the stationary wedge 83 mounted with- ,in the box 40 and usually 'made rigid with ing said plunger to enter its, bore and com` press the spring 82, the tip of the plunger passing the tip of the wedge, just aboutv the time the teeth of the clutch member 51 meet the teeth of the clutch member 50 dwhich latter condition was brought-about as thearm 71 swung to the right (Fig. 4) on the @described movement of the rod 74. When the wedge-like plunger crosses the apex of the wedge 83, the spring 82is free to expand and as it does so, it impartslto the arm 7l an accelerated further movement to theright (Fig. 4) to bring the clutch member 51 into full clutched relation with the cimplemental clutch member 50' which results in throwing into action the quick feed mechanism for the work carrier 3. f y

Mounted adjacent and in rather comparative close proximity to the lever 78 is a somewhat similar lever v85 fastened to the shaft 86 also sustained by said bracket 77.

with Seid' shaft e6 isrigl the @rank aim e7 l lVhen the lever 5 is swung towardthe right speed mechanisms are thrown into action',:

means acts satisfactorily in this connectiolig4 to which is pivoted the rod 88 joined at its rear end to the outer Vbranch of the three-jA armed rocker 90 which is an exact counterpart of the rocker-69. The intermediate arm of this rocker 90 is lforked and the f70 branches of its fork have studs91 toentenj t-he peripheral channel of the shiftable clutch member 60 while the inner branch has e' spring plunger 92 cooperative with the'fixed wedge 93 on th bearing 94 in the box 40. .7,

the rod 88 is moved to thev rear s o that its" vintermediate arm can be swung over rstbyv hand and thereafter by the spring of thel plunger 92 in the manner exactly as de- 8,0 scribed, to cause the clutch member 60 to e11, gage the clutch member 61 and thereby as" set forth cause the rotation of the worm 5.6. lVhen both levers are thrown forward 0r 'to the right in Fig. 2 both the quick andslow -35 but the slowl speed mechanism accomplishes nothing until the quick speed is thrown outf;I of operation. I As will be inferred the two levers 78 and 85 can be operated by hand, although the quick feed controlling lever 78 is normally under lock as will hereinafter appear.- Irr addition to this the two levers are.'-autof--4 matically operated through means movable 95 with the carrier 3 and the disk 95 equipped with one-or more dogs, cams or equivalent',l

Said disk 95 constitutes a cam, being 'rigidly fastened in some desirable manner to'th forward end of thecam drum shaft-.7 from. whichy it will be clear that said diskl 95 rof tates in unison with the cam drum 6'.. v Y, y The eifects of the quick andslow feed" mechanisms, as will bennderstood, .are'applied to the sectional shaft 54, the sections, of which during work are normally clutched` to each other, as will hereinafter appesa." To theinner or front sectionfof said shaft I; 54 is connected a pinion 542 in mesh with thel spur gear 55 rigid with the camdrum shaft 7 as' shown for instance in Figs. 2 and'4. It, therefore, follows that as the speedof the?.L shaft 54 variesthe speed of the'shaft7 anddz'tA hence of the drum 6throughtheintermedi" ate described connections will be correspo`nd-`l ingly changed so as to regulate the feed ofi the reciprocatory carrier 3. .-.1 In the diagrammatic Fig. 8 Ihaveshown. the disk or cam 95, the carriage recipro- 1 eating drum 6, thel stud 10, thev two levers f, 78 and 85 and certain cooperating devices."rv including a series-of dogs 96, 97, 98, 99,' 100 and 101 on the disk v95. These dogs, cam'. members orvtap'pets 96 to 101 'texcept'zthe 12,51 dog 97)A are not onl7 removably mounted but are adjustable to' vary'their points -of* action against the respect-ive levers 78 andi- Tv 85. This Fig. 8 shows one completecycle4 o# movement of the parts and in it thearrows 130 bevel surfaces 108 and 109.

indicate the direction of travel of the respective parts. As shown in Fig. 7 these dogs straddle the periphery.of` the disk 05 and are (except the dog 97) adjustable;circumferent-ially of said disk. They may be held in their adjustedpositions by screws as 102 adapted to enter the annular groove, 103% nea-r the periphery of said disk The dog orepcam 97 isthe prim ary or master cam, and in the present instance as virtually stated, is not adjustable; it may be held rigidly in position by a pin, rivet 10ft or in some other suitable manner. Referring again to Fig. 8 the two levers 78 and 85 are shown as occupying .their operative or shifted positions or that they assume when the quick and slow feed mechanisms are thrown into action, although when they are thus shifted, the slow feed mechanism is accomplishing nothing, being operative only when lthe lever 78'is-in its initial position as shown' in Fig.` 2 for example. levers as may be inferred are automatically moved from their shifted to their originall positions by the dogs or cams 96 to 101 inelusive, and for this .purpose they uiavbe provided with pins or-studs 105 and 106 to be engaged by said dogs. Said levers can also be operated by hand. Both. pins 105 and 106 are yieldingly mounted; i will hereinafter describe the mounting of the pin. 105 whichis exactly like that of the pin 108. The dog 96 is provided with an active sur- 1face` 107 shown as beveled. 1t will be assumedfthati'the parts are shown in the' positions representedin'F-ig. 8; as a consequence the work carrier 3 willbe `fed at its high s eed. As the disk 95 rotates this beveled surface 107 will strike the pin 106 and shift the lever 85 to its original position7 lsaid lever through the rod 88 and connections described moving the clutch member 60 out of engagement with the clutch member 01. The master dog or cam 97 has two oppfosite As the disk 95 i. continues to rotate, the bevel surface 108 will act against the pin 105 in-such manner las to return the lever 7 8 to its initial' position, whereby said lever on ,such movement can through the rod 711 and intermediate described connections7 disengagc the clutch member 51 from the clutch 50 and wholly arrest themovement of the work-carrier 3. "When the work-carrier 3 comes to a` state of rest, the pin 105 will be against the wedge 0r bevel surface 108 near" the outer end thereof and the wedge orbevel surface 109 on the final part of the movement of the cam disk 95 will engage the pin 106 andslightly shift'said lever 85 but not sulii-v ciently to effect through the described connections, theengagement ofthe clutch 1nem ber 60 with the clutch member 61. This cani or dog`97 presents a convenient means for locking the lever 78 normally against against the pin 100. It will be evident that whenthe pin 105 is against the bevel surface 108, the lever78 cannot be shifted unless the pin 105 be disengaged from said bevel surface 108 or what is the same thing,` the cam dog` 07 of `which said bevel face forms a 75 part. The pin 105 (Fig. 7) as shown is slidingly fitted within the sleeve 110 which extends freely through counterbored opening 111 near the upper or outer end of the level the outer end of said sleeve 110 80 -bei closed by the thimble 112 which is threaded into said sleeve 110 and which virtually forms a rigid part thereof. Between the thin'ible 119. and the pin 105 `is interposeff! the coiled spring 113, the thimble and pin. being bored to receive the terminal portions of the spring which acts toyieldingly backup the pin 105. The sleeve 110 constitutes a. convenient carrier for the pin,

being in itself yieldingly mounted, being circumferentially reduced to present a shoulder 114, the circumferentially reduced portion being surrolmded by the coiled push spring 1-1'5 bearing against said shoulder and also against an abutment consisting in the present case of the inner wall of the ,counterbored portionof the hole or opening 111, the spring` 115 exerting constant tendency to advance the sleeve or carrier and necessarily v the yield'ingly mounted pinw'OO 105 associated therewith.

ljivotally suppoirtedV between its ends near the handle end of the lev-er78 is the short lever 117. As a matter of fact the upper branch of said level- 117 can be grasped at 105 the same time that the handle of said lever 78 is. The lower'branch of the short lever 117 is forked to fit the annular groove 118 in the thimble 112. Vhen the operator grasps the handle of the lever 78 to move 110 the same forward, or to the rightzin Fig. 8 the palm of his hand or some other part thereof willpress the upper or long branch of the' short lever 117 inward and the lower or short branch outward, thereby retracting the sleeve 110, and as a consequence the pin 105 so that the pin will be carried free of the camA or dog 97, the lever 78 as a consequence being releasedby the cam or dog 97,

so that it can be swung forward to throw 120 the high speed mechanism into action in the manner already described. As soonA as the lever 78 is shifted the disk 95 commences' to rotate also in the manner set forth and as said disk turns the bevel face 109 rides 125 against the pin 106 and shifts the lever 85 to throw the clutch member 60 into clutched relation with the clutch member ,61. It will be assumed that the disk is being rotated (Fig, 8); when it has moved a ncertain dis- 130' 78 on such movement through the described primary dog 97.

parts disengaging the clutch member 51 from the clut-ch member 50, the clutch member 60` however, still being in engagement with the clutch member G1, so that as4 aA consequence the work carrier will be driven at its low speed. Subsequent -to this point the'bevel surface 120 of the cam or dog 99 will act against the pin 105 to again shift the lever 78 and throw the hirrh speed mechanism into action. Followimgr this the bevel surface 121 of the dog 100 will engage the pin 105 to stop the quick' speed, the slow speed, however, still remaining,F in action. The bevel surfaces 122 will then engage the pin 105 and again shift the lever 78 to throw in the high speed feed mechanism beyond which point the bevel surface 107 will en- `rage the pin 10G to return the lever 85 to its primary relation, this continuing until the bevel surface 10S' engages the pin 105 to return the lever 78 to its initial position 11nd thereby stop the feed. The dogs in question may he increased or decreased as will be inferred. In Fig. 8 I have shown by dotted lines a dog 123 just like the other dogs and which has bevel surfaces 124 and 125 to simultaneously return the two levers T3 and 85 from their shifted to their original positions. l

It will be noticed that the auxiliary dog 90 and -98 to 101 inclusiveaand the dog` 123 extend out from the periphery of the disk 95 a greater distance than the master or Some of these auxiliary dogs act to return the lever 73 from a shifted to an initial position. The object of this difference in extent between the auxiliary dogs and the main or master dog is this: The lever 7S is initially shifted by hand by the retraction of the pin 105. It is possible that an attendant may inadvertently hold the lever 117 in its shifted position; in this event the dog which should return said lever to its original position will engage the pin 105, notwithstanding' the fact that said pin may be in its retracted position, and knock the lever 78 out of the operator`s hand and return the same to its primary position.

During normal operation of the machine the sections of the shaft 54 are connected rotatively with each other, and for this pur pose a clutch may be utilized (see for eX- ample Figs. 2 and 4). This clutch consistsof sections 130 and 131, the section 130 being connected with the rear section of said shaft by pinning or otherwise, while the clutch section or member 131 is splined to the forward or front section of said shaft. In both Figs. 2 and 4 the members or sections 130 and 131 are clutched together, by virtue of which when the rear shaft section 54 is driven through the intervention of,l

either the quick or slow feed mechanism the rear section of said shaft 54 will be rotated to effect the turning' of the drum 6 and cnbranches of which have studs 134 vtting a' circumferential channel in the clutch member 131. Pivoted to the forward end of .said rod 132 is the crank arm 135 fastened to the shaft 136, the crank arm 135 being inclosed in the bed 2. Fastened to the sha ft 136 eXteriorly of the bed 2 is the hand lever 135 shown as occupying its normal position in Fig.: 2. When the hand lever 135 is swun; to the right in Fig. 2 the clutch member 131 through the described parts will be disconnected from the' clutch member 130 thereby throwing the drum 6 out of operar ative relation with the power driven or rear section of the shaft 54. Connected With-,the forward section ofthe shaft 54 (Fig. 10) is a spur gear 137 in mesh with a spur gear 13S ri ,gid with the shaft 139 supported within the base or `bed 2. Rigid with the spur gear 133 is the bevel gear 140 in mesh with the bevel pinion 141 at the inner end of the stub shaft 142 supportedv by said bed 2, the

two bevel gears being within the-bed. The, 5 outer or extended end of the shaft 142 is shaped by beingr squared or otherwise as at 143 to receive a hand crank. work carrier or table 3 the clutch member 131 will be disconnected from the clutch member 130 by the operation of the lever 135 in the manner already described after which the hand crank will be connected with the squared end 143 of the stub shaft 142. The shaft 142 can then be rotated to effect through the described gearing the` rotation of the forward section ofthe shaft 54 and through the latter and the described caring the rotation of the shaft 7 and cam rum 6 and necessarily the movement either forward or backward of the work carrier 3.

The tappets or cam members 97, 120 and 122 are provided upon their outer surfaces with rearwardly beveled faces 150, 151 and 152 respectively, the function of which will now be explained. As I have set forth there are times when the work carrier 3 should be adjusted manually, and in accomplishing this oflice the disk 95 is sometimes vturned forward .and at other tmesfvturned back- To adjust the ward, These beveled surfacesfIO, 151 and' ward, and in this manner the backwardfad tion.

l the justment of the disk 95 can be accomplished Without doingany injury. it will be remembered that I have stated that the two pins 105 and 106 are'similar in' mounting. Imight state. that-.while the pin 105 is provided with an op# ating lever as 117, there is no occasion for such an operating lever in conjunction with the pin 106.

It is important that the speed of the reciprocatory 'or slidable work carrier`3 be reduced duringl milling or approximately coincident with the reverse in movement of said carrier.' that is to say at practically the conclusion of the advance and the commencen'ient of the retraction of said carrier, by virtue of which the milling or equivalent tool is prevented from injuring= the work. This result I can obtain-vin various ways, althougl'i the cam 6 has been found very satisfactory in this respect. the movement of the 1/arrier being' perceptilnjj; reduced at about the time the stud 10 leaves spiral. portion l1 and enters the spiral portion 12 as shown in Fig. 5. This slowing down in movement of the carrier 3 at the time indicated occurs when either the high or low speed feed mechanism is in ac- When the slow feed mecl'ianism is in evident that substanoperation, it will be the speed of tially at the point of .reverse the'carrier is further reduced.

lll/'hat I claim is:

l. In a machine of the class described, the combination of a power transferring member, a second power transferring member having,- a. constantclutch connection with the first power transferring member, means for driving the first power transferring member at a greater speed than the second power transferring member and for stopping them both at predetermined points, and a movable member having a driving connection with the first power transferring member.

2. In a machine of the class described, thecombination of a reciprocatory carrier, a power transferring member having a driv- 'stant clutched connection Awith equivalent action tire .levers for ing connection with the carrier, a second power transferring member having a conthe first power transferring member, and means for rotating the power transferring members at different speeds.

3. in a'machine of the class described, the combination of a traveling` carrier, a power transferring member having a driving' connection with said traveling carrier, a second power transferring member having a pawl and ratchet constant clutched connection with the first power transferring member, and means for driving the power transferring members at different speeds.

4l. In a machine of the class described, the

lcombination of a traveling carrier, means involving` quick and slow speed mechanisms 'or reciprocating the carrier, levers for independently, controlling said mechanisms, and a rotary disk provided with a series of peripheral dogs having beveled portions disposed in opposite directions, the levers havingI pins engageable by the beveled portions as the disk rotates Vto mov@ the levers opposi tely, certain of the dogs extending outward from the periphery of the disk a greater distance than another dov'.

' 5. In 'a machine of the class described, the combination of a traveling carrier, means i11- volving quick and slow speed mechanisms for operating the carrier, independently acautomatically controlling said mechanisms, and a rotary disk provided withv peripheral dogs, the levers having pins engageal'ile 'by said dogs to shift the levers, one of the `dogs being initially disposed in the path of one of the pins, and means for retracting said last mentioned in.

In testimony' whereof a X my signa ture in presence of two witnesses. l

BENGT M. W. HANSON. Witnesses:

WV. M. S'ronns, C. M. GnLLenr. 

